Fluid proportioning system



y 1960 A. BIBER 2,938,650

FLUID PROPORTIONING SYSTEM Filed Sept. 18, 1958 2 Sheets-Shet 1 INVENTOR ATTORNEY May 31, 1960 BIBER FLUID PRQPORTIONING SYSTEM 2 Sheets-Sheet 2 Filed Sept. 18

ATTORNEY FLUID PROPORTIONING SYSTEM Albert Biher, Pittsburgh, Pa., assignor to Gulf Research & Development Company, Pittsburgh, Pa., a corporation of Delaware Filed Sept. 18, 1958, Ser. No. 761,744

Claims. (Cl. 222-70) This invention relates to a fluid proportioning system and more particularly to a proportioning system that is adapted to blend and dispense a plurality of gasolines in selected proportions.

The growing trend in the automobile industry for higher horsepower necessitates increases in the compression ratios of auto engines which in turn requires a higher octane rated gasoline to counteract the greater knocking tendency of the higher compression ratio engine. This continuing increase in compression ratios, with attendant higher operating octane number rating, has created a wide divergency between the octane requirements of the earlier model automobiles as compared with the newer models. Heretofore most service stations have ofiered only two grades of gasoline for sale, each grade having a relatively different octane number rating, that is, one grade possessing an octane rating suflicient, normally, to prevent knocking in automobile engines that exhibit the most extreme knocking tendencies, and a second quality gasoline adapted to function without knocking in automobile engines having substantially less knocking tendencies. By far the greatest number of autos today have octane requirements which lie between the two grades normally marketed; however, to avoid knocking in these auto engines, the motorist is forced to purchase a gasoline of considerably higher octane rating than the minimum required. In order to alleviate this situation, gasoline can be marketed intermediate in quality between the two grades normally marketed. These intermediate grades of gasoline can be marketed by installing additional storage and pumping facilities in existing service stations, plants and refineries, but a considerable saving. is eflected by utilizing the existing dual storage facilities and by marketing blends of the present higher and lower octane gasolines blended at the service station at the time of purchase.

Various gasoline proponioning and dispensing pumps have been proposed as a solution to the blending of gasolines at the service stations, but such pumps are normally relatively expensive, since they usually involve several duplicate parts, and in that they are sufliciently unconventional as to present substantial problems of manutacture and supply. Adjustable proportioning valve devices have also been proposed for blending of gasoline at the service station, but difiiculty is usually encountered in such systems in maintaining a constant proportion of component gasolines in the blend. This is due to an independent variation in pressure differential across the respective proportioning valves that results primarily from independent variation in the respective tank levels.

In accordance with the present invention, a relatively low cost blending and proportioning device is provided that is adapted for use with the standard gasoline dispensing systems currently used and offered to the trade, without substantial alternation or redesign of such systems.

The present invention includes a main supply conduit, a plurality of branch supply conduits connected to the main supply conduit and to separate sources of supply ilited States. Patent The invention also includes proportioning means that 7 ice comprises a rotating valve associated with one or more of the branch supply conduits in the direction of the main supply conduit, which maintains a constant proportion of component gasolines in the blend irrespective of independent variation in the respective tank levels. A positive displacement dispensing pump is connected on the suction side to the main supply and blending conduit and to the dispensing conduit on the discharge side. A substantially constant speed motor drives the positive displacement pump, and bypass means is provided whereby the pumped fluid, in excess of the amount that can be discharged from the dispending pump into the dispensing conduit, is recirculated from the discharge side of the pump to its suction side.

The invention further includes a hydraulic motor operatively associated with the dispensing conduit and means associated with the said hydraulic motor adapted to drive the proportioning means in such a manner that a total of one volume of fluid is caused to flow through the proportioning valve for each volume of fluid passed through the hydraulic motor. The invention also includes a valve in the dispensing conduit adapted to control fluid flow therethrough.

Referring to the drawings, there is shown in Figure l a schematic diagram partly in section of a gasoline proportioning and dispensing system embodying the principles of this invention.

Figure 2 is a front elevation partly in section of a rotating valve proportioning device for use in combination with Figure 1.

Figure 3 is a perspective view of the proportioning device of Figure 2.

Referring to Figures 1 and 2, in which like parts have been designated by the same numerals, operation of a rotary-type positive displacement pump 2 causes a reduction in pressure on the inlet or suction side of the pump. Atmospheric pressure acting on the gasoline in tanks A and B, indicated by legends in Figure 2, causes flow of these fluids from the tank through supply conduits 3 and 4 toward rotating valve members 5 and 6, which alternately and/or simultaneously open or close off conduits 3 and 4, respectively, at predetermined intervals. The fluids from tanks A and B are caused to flow toward pump 2 in a fixed proportion, the proportion being dependent upon the interval in which the valves 5 and 6 remain open to the flow of fluid from conduits 3 and 4, respectively.

The gasoline from tanks A and B are-blended on the discharge side of valves 5 and 6 in conduit 16, and the mixture then passes into the main supply conduit 17 toward the suction side of dispensing pump 2 which is con nested in series with conduit 17. Pump 2 is driven at an essentially constant speed by electric motor 18. The blended fluid is conveyed from the suction side of pump 2 by rotation of vaned pump rotor 19, into the discharge side of the pump, and then into dispensing conduit 20. Dispensing pump 2 has a capacity such that it will pump fluids at least as rapidly as, and usually more rapidly than, the maximum rate at which it is dispensed from the system. The volume of fluid that is pumped through the pump in excess of the volume dispensed from the system is recirculated through bypass conduit 21, and through spring-loaded pressure relief valve 22 to the suction side of pump rotor 19.

Connected in series in dispensing conduit 20'is an air eliminator 23 which facilitates separation of air bubbles from the fluid before the fluid is passed through 'ineter 24, the meter being also connected in series in dispensing conduit 20 downstream of the air eliminator. Air bub: bles separated from the fluid in air eliminator 23 pass with some fluid through a small diameter conduit 25 into chamber 26 from which air is vented to the atmosphere The .excessfluid in chamber duit 20 is mea'suredbyflow through meter 24 'which comprises a hydraulic motor having arotary shaft '28 whose rotation is'directly proportional to the volume of liquid passed .therethrough. vThe rotation-of shaft 28 is translated'into totalgallons and total "sales price by a-system of gears in variator and computer-counter 29.

In the illustrated embodiment, drive shaft 34 and a pair of bevel gears 30 comprise the means associated with the hydraulic motor (meter 24) adapted to drive gear 7 of the proportioning device. Gear 7 frictionally drives 'gears'8 and9 (see Figs. 2 and 3), said gears '8 and "9 being movably mounted on shafts 10 and 11, respectively. Shaft 13 is connected to a timing gear 12 that meshes with one revolution gear 13, gear 13 being conneoted to rotating plug valve 5 through detent cam '15 on shaft 14, and gear 9 being connected directly to rotatingplug valve 6 through shaft 11. It may be seen that for each revolution of gear 9, rotating plug valve 6 will also move through one revolution thereby opening and closing conduit 4 to fluid flow at equal intervals. The volume of fluid flow through valve 5 is dependent upon timing gear 12 and in turn the speed of rotation of gear 8. The opening and closing of rotating plug valves 5 and 6 and the rotation of the meter shaft 28 are so interrelated -that for each unit volume of fluid that is caused to flow through meter 24, a total of one unit vol'umeof fluid will be caused to flow from. branched supply con- 4 rotation of .gear 12 through. shaft 10. As gear 12 turns, the teeth on one-half of the circumferential edge of the gear will mesh with gear 13 causing said gear 7 to turn one revolution for one-half revolution of gear 12, rotating plug valve 5 being connected to gear 13 by shaft 14 will also turn one revolution. Figure 3 shows the one revolution gear 13 just before demeshing with gear 12. As these gears demesh, valve 5 will be fully open to the flow of. fluid through conduit 3. Rotating valve 5 will remain fully open until gear 12'remeshes withgear 13. As illustrated, detent cam "15 will engagewith cam rider 35 in detent 36 as gear 13 is demeshed from gear 12 thereby holding rotating valve5 fully open to the flow of fluid.

Rotating plug valve 6, being connected directly to gear 9 by shaft 11, will alternately open and close conduit 3- to the flow of fluid at equal intervals.

As hereinbefore described, gears 8 and 9 are movably mounted on shafts 10 and 11, respectively. Means are provided whereby these gears may be positioned relative to the central axis of drivinggear 7 .on their respective shafts. It may be seen that by altering the distance of the point of contact of gears Sand 9 from the center of driving gear 7, a continuous speed variation 'may be obtained, thereby changing the speed of rotation duits 3 and 4 through valves 5 and 6 to main supply Conduit 17.

Continuing the detailed description of the system as shown in Figure 1, the blended fluid passes downstream from meter 24 through a check valve (not numbered) then through visi-gauge 31 and out of the system through dispensing nozzle 32 at a rate controlled by manually operated spring-loaded dispensing valve 33.

h For a clear understanding of the proportioning device further reference is now made to Figures 2 and 3 in which like parts have been designated by the same numerals. As may be seen, driving gear 7 is mounted on shaft 34. Gears 8 and 9 frictionallyengage with the face of driving gear 7 and are movably mounted on shafts 10 and 11, respectively. Rotating .plug valve 6 in conduit 4 is connected directly to gear 9 through shaft 10 in such a manher that for'each revolution of said gear, rotating plug valve 6'will likewise turn through one revolution. Timing gear 12 is connected to gear 8 through shaft 10, said tim- 'ing gear meshing with and driving one revolution gear 13. The teeth of geary12 are deposed substantially on one-half of the circumferential edge of the gear,the"remainder of the said circumferential edge being without teeth. 'Thus it may be seen that only one-half of the circumferential edge of gear 12 will mesh with gear 13; however, gear 13, having the same number of teeth as those deposed on one-half of timing gear 12, will be caused to turn one revolution as timing gear 12 makes substantially one-half revolution. One revolution .gear 13 in turn causes rotation of plug valve 5 in conduit 3, said one revolution gear being connected to valve 5 by shaft 145 Detent cam 15 is interposed between one revolution gear 13 and rotating plug valve 5 on shaft 14. Spring-held cam rider .35 engages with detent 36 on cam "15. Gears 8 and 9 are mounted on their respective shafts in such a manner that valves 5 and 6 will either openalternately or simultaneously, thus preventing the complete shutoff of fluid to pump 2 which would starve the pump and cause cavitation.

In operation, rotation of shaft'34 causes clockwise rotation 'of driving gear 7 which in turn causes counterclockwise rotation of gear '8 and clockwise rotation of "gear-9, "gears 8 and 9 being frictionally engaged with gear '7. Rotation of gear 8 imparts a counterclockwi'se of valves 5 and 6, respectively; that is, the farther gears 8 and '9 are from the central axis of driving gear 7, the faster gears 8 and 9 'will rotate, and in turn the faster valves 5 and 6 will rotate, valve 6 directly and valve 5 through gears 12 and 13.

As can be seen, the volume of fluid that will flow through valve 5 is dependent upon the speed of rotation of gear 8. It is essential to prevent cavitation of the positive displacement dispensing pump. To this end the speed of rotation of valve 6 may be varied to insure the alternate opening of this valve with respect to valve 5. It

is obvious therefore that the proportion of fluids from tanks A and B may be varied by simply changing the speed of rotation of gear 8 thereby changing the volume of fluid flow through valve 5 in relation to that volume of fluid which is caused to flow through valve 6.

It will be appreciated that placing of the proportioning device upstream of the dispensing pump is advantageous in that such placement permits use of standard gasoline dispensing pumps and blending pumps Without substantial redesign. It will also be appreciatedthat the herein disclosed invention permits passage of the blended prod- 'uct through the dispensing pump, thereby avoiding ab normal loading of the bypasssystem attendant to placing the proportioning valve downstream of the dispensing pump. The herein disclosed invention also permits pumping of the two fluids in varying proportions using both a single dispensing pump and a single flow meter. By use. of the herein described proportioning system, cavitation caused by independent variation in the respective tank levels is effectively minimized.

In the illustrated embodiment of Figure 1, the means associated with meter 24 and adapted to drive gear 7 is shown for purposes of illustration as shaft 34. The invention, however, is not limited to such structure for any other suitable means for transmitting the rotary motion of shaft 28, either directly or indirectly, to gear 7 can be used. For example, where the proportioning device is relatively remote from meter 24, it is advantageous that the rotary motion be transmitted over most of the distance between the meter and the proportioning device by means. of a pair of self-synchronous, or so-called Selsyn, electric motors, or equivalent means. Such motors can be interposed in place of shaft 34.

Instead of employing rotating plug valves 5 and 6, as shown in Figures 2 and 3, other valves capable of performing the same function can be used. For example, a rotating ball valvernay be substituted for the rotating plug-type valve. Also, the disclosed system is adaptable in an obvious manner to the blending of more than two fluids; that is, other valves arranged as a unitized assembly made up of a valve, detent cam and one revolution gear, can be operatively associated with the timing gear.

It will also be apparent that two or more fluids, other than gasoline, can be blended in a fixed predetermined proportion using the herein described invention. In addition, changes in form, size, arrangement of parts, operation and mechanical details may be made.

It is therefore obvious that these and other modifications can be resorted to without departing from the spirit and scope of this invention. Accordingly, only such limitations should be imposed as are specifically set forth in the appended claims.

I claim:

1. In a fluid proportioning system having a main supply conduit, a plurality of branch supply conduits connected to said main supply conduit and to separate sources of supply, proportioning means comprising a rotatable valve in each of said branch supply conduits, a valve driving gear operatively connected to each valve, a rotatable gear for driving the valve driving gear connected to each of said valves and means for changing the point of contact of each of said valve driving gears with respect to the central axis of said rotatable gear, whereby the speed of rotation of the said rotatable valves in each of the said branch supply conduits may be changed.

2. In the fluid proportioning system of claim 1 wherein the operative connection between at least one of said valve driving gears and one of said rotatable valves comprises one gear having teeth on substantially one-half of its circumference, the remainder of the circumference being without teeth, and a one revolution gear meshing therewith, said partly toothed gear being operatively connected to one of said valve driving gears and the said one revolution gear being operatively connected to one of said rotatable valves, whereby the said rotatable valve will be caused to turn one revolution as said partly toothed gear meshes with said one revolution gear and thereafter remain fully open to the flow of fluid while the said one revolution gear is demeshed from the partly toothed gear.

3. In the fluid proportioning system of claim 1 where in the operative connection between at least one of said valve driving gears and one or" said rotatable valves comprises a one revolution gear operatively connected to said rotatable valve, a timing gear having teeth on substantially one-half of its circumference, the remainder of its circumference being without teeth, said timing gear meshing with said one revolution gear and being driven by one of the said valve driving gears in such a manner that the volume of fluid flowing through said rotatable valve is caused to be substantially proportional to the speed of rotation of the valve driving gear.

4. In the fluid proportioning system of claim 1 wherein the rotatable gear for driving the valve driving gear is frictionally engaged with the said valve driving gear.

5. In the fluid proportioning system of claim 1, wherein the operative connection between at least one of said valve driving gears and one of said rotatable valves comprises a one revolution gear operatively connected to said rotatable valve, a timing gear having teeth on substantially one-half of its circumference, the remainder of its circumference being without teeth, a restraining means interposed between said revolution gear and said rotatable plug valve, said restraining means being effective to maintain said valve in one position whenever said revolution gear is out of engagement with said timing gear, said timing gear meshing with said one revolution gear and being driven by one of the said valve driving gears in such a manner that the volume of fluid flowing through said rotatable valve is caused to be substantially proportional to the speed of rotation of the valve driving gear.

References Cited in the file of this patent UNITED STATES PATENTS 1,964,028 Boynton et al. June 26, 1934 2,057,226 Bleecker Oct. 13, 1936 2,065,128 Eisinger Dec. 22, 1936 2,743,843 Bliss May 1, 1956 

